Die roll forming and finishing machine



Aug. 30, 1966 H. A. GREIS 3,

DIE ROLL FORMING AND FINISHING MACHINE Filed March 30, 1964 2 Sheets-Sheet l INVENTOR HOWARD, A. GREIIS BY Wf ATTORNEY Aug. 30, 1966 H. A. GREIS DIE ROLL FORMING AND FINISHING MACHINE Filed March so, 1964 2 Sheets-Sheet 2 INVENTOR HowARq A. GREIS 3 BY ATTORNEY WWW United States Patent Ofiice 3,259,161 Patented August 30, 1966 3 269 161 DIE ROLL FORMING ANl) FINISHING MACHINE Howard A. Greis, Holden, Mesa, assignor to Kinefac Corpltliratirtan, Worcester, Mass, a corporation of Massae met 3 Filed Mar. 36, 1964, Ser. No. 355,589 12 (Claims. (U. 72-98) This invention relates to a new and improved cylindrical die roll forming and finishing machine, and the principal object of the invention is to improve the operation of roll forming and finishing while at the same time providing a more economical and easier operated and adjusted machine at less original cost.

One of the main improvements over the prior art resides in the use of a very few drive points or connections as compared with machines of the prior art, for better control over the relative positions of the two dies and for less backlash between dies, and this in turn provides torsional rigidity and a shorter path from the prime mover through to the dies. Also less actual material is used to build the machine and there are less moments in the gear train and the power drive train, and less horsepower loss.

In the prior art, to provide for through feeding and the in and out motion of the spindles for in-feeding, a relatively long double universal joint system has been used, and when these are operated in skew relation, conventional cross-axis universals do not transmit constant angular velocity unless the universals are matched, i.e., placed in correct phase with each other, and this in turn causes angular relationship of the dies to be continuously varying and thereby producing drunken threads and causing reduced die life.

It is a primary object of the present invention to eliminate angular velocity errors, excessive looseness of parts, and to substitute a torsionally more rigid connection between the dies, and this is done by eliminating one of the universal joints and providing a short shaft upon which the cylindrical die is mounted, the shaft having an integral ball with a universal joint connection to a driving gear which is hollow and cylindrical in form and surrounds the ball. This novel construction eliminates a part of the prior art universal joint construction, shortening the torsional path, and also reducing the number of wear points. This in turn provides for a more compact gear system and because of the foregoing the new machine is easier to operate especially using through feed for long rods, because the novel gearing in the present invention does not interfere with the feed.

A further object of the invention resides in the provision of a pair of interpivoted heads moving about a pivot axis, there being a die on each head, with means to pro vide for adjusting the same where desired and particularly in a skew arrangement for forming threads, the construc tion including a draw bar for connecting the heads and drawing or holding the same together about said pivot axis applying a great force through the dies to the work; and the provision of means for quickly retracting both heads from the work to free the work completely at both sides for easy advance or feeding of the work; and the provision of compensation for the growth of the work as it is formed and also for Wear on the blade due to the pivot action of the aforesaid heads moving together under influence f the draw bar.

Another object of the invention resides in the provision of mechanism of the class described which when used for in-feed, permits die-work contact point to rise during the rolling cycle and thereby at least partially compensating for part diameter growth, thus reducing blade pressure and blade wear. Other objects and advantages of the invention include a novel taper adjustment for the heads, and a unique blade mounting and adjustment means to give extra rigidity of the rolling position during through feed, and easy adjustment of the blade.

Other objects and advantages of the invention will appear hereinafter.

Reference is to be had to the accompanying drawings in which:

FIG. 1 is a view in front elevation, parts being broken away and in section for clarity of illustration;

FIG. 2 is a plan view, looking in the direction of arrow 2 in FIG. 1;

FIG. 3 is a section on line 33 of FIG. 2;

FIG. 4 is a view in elevation, looking in the direction of arrow 4 in FIG. 2, parts being removed for clarity of illustration;

FIG. 5 is a section on line 5-5 of FIG. 2;

FIGS. 6 and 7 are sectional views taken respectively On lines 6-6 and 7-7 of FIG. 3;

FIG. 8 is an enlarged section on line 88 of FIG. 4;

FIG. 9 is a sectional view illustrating the adjustable limit stops for the swinging motion of the heads, and

FIGS. 10 and 11 are enlarged sections on the lines respectively 1010 and ill-11 of FIG. 8.

Referring now to FIGS. 1| and 2 it will be seen that the entire machine can be appropriately mounted on any kind of a table or base such as is indicated by the numeral 10. A pair of spaced bearings 12, 12 are provided on this table and these hearings between them mount a shaft 14, see particularly FIG. 8. Mounted to swing on this shaft are a pair of arms or heads 16 and 18- using appropriate bearings, etc. as shown in FIG. 8. These arms 16 and 18 are generally in a C shape but they are provided with opposed straight faces as shown in FIG. 4 at Zil, 20 upon which the dies themselves are mounted, the dies being indicated by the reference numeral 22. These dies are of course alike and are complementary to each other, and in FIG. 1 the work is shown at 24 and the blade which supports the work at 25.

These dies are rotated while held in desired angular relationship by the gear train and the diametral relation for through feed, or the dies are held parallel with varying diametral relation for in-feed, in order to form and finish the workpiece 24 which passes between them in a direction generally parallel to the shaft 14. As the members 16 and 18 are pivoted about shaft 14 toward each other, they impress the dies upon the work very powerfully and this is done by means of a draw bar which is generally indicated at 26 which may operate under any kind of pressure or power or held fixed such as for instance hydraulic, and which is also provided with an adjustment device in the form of a screw thread as shown at 28 for the purpose of adjusting the limit of motion of the heads 16 and 18 to and from each other. When the heads 16 and 18 swing away from each other, the dies release the work 24 simultaneously and completely at both sides thereof so that it is easily forced through the machine and out; or if through feed is being used, a gap therein is provided as long as is predetermined by the dwell of the heads 16 and 18 in their spaced-apart positions. Each head 16 and 18 has a pair of spaced feet which pivot on the shaft 14, and can be adjusted for die taper as will be later described.

The dies are each held in a separate block, these blocks being alike and indicated at 30, 30. Each block mounts by appropriate bearings a shaft 32 and can be adjusted on its face support 20, 20 by means of any desired or convenient apparatus such as the holding bolts 34, see particularly FIG. 3. It will be seen that the blocks can be adjusted in a skew relationship about a pivot 35 so as to position the dies 22, 22 angularly with respect to each other to form threads. Appropriate stops or the like 36 (see FIG. 5) are provided for the purpose of maintaining 3 the adjustment and also for forming stops for setting the die blocks 30, 30.

The gear train comprises a prime mover (not shown) which may drive a belt, sprocket or the like 38 which in turn drives the pulley 40. This pulley drives a main gear 42 which is in turn in mesh with separate gears 44- and 46 (see particularly FIG. 1). In turn, gears 44 and 46 drive relatively small spur gears 48 and 50. These gears individually mesh with separate universal joint gears 52 and 54. This train of gears is maintained on parallel axes and they therefore always operate with uniform velocity. Gears 52 and 54 are held parallel with relation to the axes of gears 48 and 50 by the intermeshing of the gear teeth and also by the plates 58.

Referring now more particularly to FIGS. 6 and 7 where the universals are shown, it will be seen that the gear 54 (also 52) is a hollow cylindrical spur gear and it surrounds a ball-like member 56 which is integrally of fixedly mounted with respect to its shaft 32. Face plates or the like 58 are used to finish the assembly and these have ball-contacting surfaces mating with the ball. There is a cylindrical pin 60 which extends diametrically through the member and it engages at its squared ends in internal axially arranged recesses 62, 62 at diametrically opposed points within the gear 54. It will be seen therefore looking at FIG. 7 that the gear 54 can oscillate in a clockwise or counterclockwise direction as viewed in FIG. 7 while still being driven by the square ends of pin 60 engaging the flat walls of the recess. At the same time it is to be noted that pin 60 is cylindrical and is located in a cylindrical diametrical passage through the ball so that the gear 54 is free to move in a direction which may be described as clockwise and counterclockwise looking at FIG. 6.

It is to be understood that the respective dies are mounted on the respective shafts 32 in fixed relation with respect thereto and that these shafts 32 and therefore the dies are rotated through the gears 52 and 54; and also it will be clear that when the shafts 32 have been adjusted in angular relationship with respect to each other, the gearing above described will still be effective due to the universal joint shown in FIGS. 6 and 7 as above described.

However, when the blocks 30 are adjusted for skew relationship, gears 52 and 54 may rise or fall depending on the particular adjustment, and therefore there are provided the supporting plates 64 pivoted at the pitch lines of the gears 44 and 46, i.e., at 66. Nuts 68 are loosened prior to adjustment, and with the plates 64 loose, the gears 48' and 50 return to correct mesh with gears 52 and 54 due to the pressure of springs 70. The nuts 63 are then tightened once more.

The shaft 14 also supports an eccentric member 72 which bears on a vertically adjustable frame 73 holding the blade 25, and vertically adjusts it according to calibration by means of the thimble 74 which turns shaft 76 and its worm 78 to turn gear 80 and the eccentric for this purpose, see FIG. 3. The frame 73 can be spring pressed for return to its lower position.

The heads can also be adjusted on an axis to vary the taper between dies. The head 18 is pivoted on shaft 14, see spaced feet 18a and 1812 (FIG. 8), and head 16 is also pivoted on the same shaft, see feet 16a and 1621. However, foot 16b of the head 16 is free to pivot in a direction perpendicular to the axis of shaft 14, on a ball-like member 80. Foot 16a can be moved because of a bushing 82 which is adjustable from a convenient point externally. Bushing 82 has a concentric part 84 (FIG. .10) supporting the heads 16 and 18 vertically. Slidable keys 86 support head 16 vertically but are free to move in their slots 88 to allow head 16 to move horizontally.

Bushing 82 has an eccentric part 90 pressing against a pin 92 that is free to slide in a slot 94. As bushing 82 is turned in the proper direction, head 16 is urged to the right, e.g., see FIG. 11, against the action of return spring 96, mounted in a frame part 98. Thus head 16 is bodily adjustable relative to head 18 while still being swingable on the same shaft.

FIG. 9 is a view showing an adjustment for the exact strike of heads 16 and 18. A block acts as a stop as heads 16 and 18 move toward each other and nut 102 acts as a stop when the heads separate. The block moves from one step to another against the action of spring 104 the tension of which can be adjusted by a nut 1196. Nut 102 is of course re-positionable on its screw support 108. This mechanism is provided for each head, see FIG. 4, and the supporting screw 108 is vertically mounted in the frame of the machine.

Thus it will be clear that a versatile, compact, and easily adjusted roll die machine has been provided which is much easier and faster to set up and operate and in which the power train has been reduced in length and parts and has been made more accurate and less expensive to manufacture and also to operate.

Having thus described my invention and the advantages thereof, I do not wish to be limited to the details herein disclosed, otherwise than as set forth in the claims, but what I claim is:

1. Die rolling apparatus comprising a supporting framework, a pair of shafts, means mounting the shafts on said framework, in cooperative relation with respect to each other, a die on each shaft for rotation thereby, said dies being arranged to operate on a workpiece between the same, a driving gear universally mounted on each shaft, torque transmitting means connecting each gear and its shaft, means driving each gear, and means to adjust the shafts and thereby the dies angularly with respect to each other.

2. The die rolling apparatus recited in claim 1 wherein the framework includes a pair of supports on which the shafts are mounted, said supports being movable rela tive to each other, and means to move said supports and thereby the shafts and dies toward each other.

3. The die rolling apparatus recited in claim 1 wherein the shaft driving means includes a gear system and means to adjust parts of the gear system to substantially eliminate backlash in the gearing upon adjustment of the shafts.

4. The die rolling apparatus recited in claim 1 wherein said framework includes a pair of movable supports, means to move said supports relatively toward each other to operate upon a workpiece between the dies and to move relatively away from each other to free the workpiece.

5. The die rolling apparatus recited in claim 1 wherein said framework includes a pair of movable supports, means to move said supports relatively toward each other to operate upon a workpiece between the dies and to move relatively away from each other to free the workpiece, said last-named means operating to move said supports generally equally so that the workpiece is completely freed from both dies upon motion of the supports away from each other.

6. The die rolling apparatus recited in claim 1 includ ing a work-supporting blade located between the dies, and including means for adjusting said blade relative to the dies.

7. The die rolling a paratus recited in claim 1 including a work-supporting blade located generally between the dies, and means for adjusting said blade, said adjusting means including an operating element extending to one side of the machine being easily accessible at a point remote from the dies.

8. Die rolling apparatus comprising a pair of interpivoted supports, a shaft mounted on each support substantially parallel to the pivot axis thereof, a die on each shaft, means for driving said shafts, said shafts being positioned so that said dies are in cooperative relationship to act on a workpiece therebetween, wherein the: workpiece has an axis of rotation no greater than slightly skewed relative to the die axes, and means for moving said supports on the pivot axis thereof to cause said dies to approach each other to engage the workpiece.

9. Die rolling apparatus recited in claim 8 including a Work-supporting means located between the dies, and an eccentric, said eccentric being operatively arranged with respect to said blade to adjust the same relative to the (lies.

1%. The die rolling apparatus of claim 8 including means moving said supports relative to each other to adjust the taper angle between the shafts.

11. The die rolling apparatus of claim 8 including means to move the supports in opposite directions from the workpiece axis to free the workpiece, said last-named means operating to move the supports generally equally so that the workpiece is completely freed from both dies.

12. Die rolling apparatus comprising a shaft, a pair of interpivoted supports mounted on the shaft, a die shaft on each support, a die on each die shaft, a drive means for each of said shafts, a universal driving connection between each shaft and its drive means, means to adjust the shafts angularly with respect to each other, and a Work-supporting blade located generally between said dies, an eccentric arranged about said first-named shaft, said eccentric being cooperatively arranged with respect to said blade so that when the eccentric is turned it varies the adjustment of the blade with respect to the dies.

References Cited by the Examiner UNITED STATES PATENTS 577,907 3/1897 Wootton 7298 1,319,143 10/1919 Dieter 72-213 1,518,721 12/1924 Wineman 72111 2,065,166 12/1936 Winwood 72-111 2,214,881 9/1940 Doherty 72-2l3 2,660,909 12/1953 Morse 72-211 2,770,986 11/1956 Bass 72-111 3,028,183 4/1962 Phillips 287-87 3,053,556 9/1962 Klocke et al. 28787 20 CHARLES W. LANHAM, Primary Examiner.

H. D. HOINKES, Assistant Examiner. 

1. DIE ROLLING APPARATUS COMPRISING A SUPPORTING FRAMEWORK, A PAIR OF SHAFTS, MEANS MOUNTING THE SHAFTS ON SAID FRAMEWORK, IN COOPERATIVE RELATION WITH RESPECT TO EACH OTHER, A DIE ON EACH SHAFT FOR ROTATION THEREBY, SAID DIES BEING ARRANGED TO OPERATE ON A WORKPIECE BETWEEN THE SAME, A DRIVING GEAR UNIVERSALLY MOUNTED ON EACH SHAFT, TORQUE TRANSMITTING MEANS CONNECTING EACH GEAR AND ITS 